Clutch mechanism



July 29, 1952 E. J. HAUBER CLUTCH MECHANISM 6 Sheets-Sheet 1 Filed Jan. l0, 1947 A TTORNE Y July 29, 1952 E. J. HAUBER CLUTCH MECHANISM A TTORNE Y July 29, 1952 E. J. HAUBER CLUTCH MECHANISM' 6 Sheets-Sheet 3 Filed Jan. l0, 1947 INVENToR.

ERM/v J. HAUBER ff f ATTORNEY July 29, 1952 E. J. HAUBER CLUTCH MECHANISM 6 Sheets-Sheet 4 Filed Jan. l0, 1947 m. R C T u m M Y W w M I H Dn J. m mi T l m m A .I E III m W E l QS Il Il. il! \\\M\ Il f mm l l Om r TIP F il. l l, VIN m| .l e m: K Q l ,wk WS July 29 1952 E. J. HAUBER 2,604,788

CLUTCH MECHANISM INVENTOR.

ERWIN J. HAUBER BY July 29, 1952 E. J. HAUBER CLUTCH MECHANISM 6 Sheets-Sheet 6 Filed Jan. l0, 1947 INVENToR.

E RW/N J. HAUBER ATTORNEY Patented July 29, 1952 UNITED STATES PATENT OFFICE (Granted under the act of March 3, 1883, as amended April 30, 1928; 3770 0. G. 757) 7 Claims.

This invention relates to improvements in clutch mechanisms.

The primary object is to provide clutch mechanism of simple and durable construction adapted to control rotation of a shaft.

Another object is to provide clutch mechanism operable responsive to the power of a rotating shaft.

A further object is to provide novel clutch mechanism wherein the power of a rotating shaft is utilized to move a clutch operator parallel to said shaft.

Another object is to provide novel clutch mechanisrn operable responsive to hydraulic power.

A further object is to provide clutch mechanism adapted selectively to effect engagement and disengagement of a driving shaft from a driven shaft.

Still another object is to provide clutch mechanism adapted selectively to effect forward and reverse rotation of a driven shaft.

Further objects and advantages of this invention, as well as its construction, arrangement and operation, will be apparent from the following description and claims in connection withthe accompanying drawings, in which Fig. 1 is an isometric view of a clutch mechanisrn, partly cut away, showing a preferred embodiment of the invention;

Fig. 2 is a longitudinal elevation thereof, partly cut away;

Figs. 3, 4 and 5 are longitudinal elevations of a portion thereof, partly cut away, showing the relative positions of components at different stages of the operation;

Fig. 6 is a section taken on the line 6-6 of Fig. 2;

Fig. '7 is an exploded isometric View of a pawl thereof, showing the staggered arrangement of the teeth of said pawl;

Fig. 8 is an isometric view of a modified form of the invention, partly cut away;

Fig. 9 is a section thereof, taken on the line 9-9 of Fig. 8; y

Fig. 10 is a section taken on the line ill-I3 of Fig. 9; and

Fig. 1l is a composite view showing the controls, in isometric view, partly cut away, connected to a clutch operator mounted on a motor, which is shown in elevation.

In general, the invention utilizes the driving power of a rotating shaft to move a clutch operator parallel to said shaft. In a preferred ernbodiment of the invention, illustrated in Figs. l to '7, both inclusive, a power shaft is provided with a right-hand threaded portion and a left-hand threaded portion, and carries a housing adapted to move axially along said shaft and over said threaded portions. This housing carries a plurality of dogs, a selected dog or dogs being adapted to engage the right-hand threaded portion and a selected dog or dogs being adapted to engage the left-hand threaded portion. These dogs, mounted in said housing for movement at an angle to the longitudinal axis of the shaft, are each provided with a threaded portion adapted to mesh with a threaded portion of said shaft. A cam bar mounted on the said housing for movement parallel to the longitudinal axis of the shaft controls the engagement of the dogs with said shaft: In one position, the cam bar holds the dogs out of contact with said shaft. When movement of the operator is desired, the cam bar is moved, thus forcing one of the dogs into engagement with a threaded portion of the shaft. Rotation of said shaft then causes an axial movement of said dog and housing, which axial movement continues until said dog reaches the portion of the cam Ibar that releases it from engagement with the said shaft. A rack and pawl construction is provided to hold the clutch operator in position when the dog is released from the shaft.

In the modified form of the invention shown in Figs. 8-11, both inclusive, an auxiliary shaft is geared to the main shaft. Both said shafts are provided with threaded portions, said respective threaded portions having a common pitch. A housing is mounted on said shafts, said housing being adapted for movement parallel to the longitudinal axes of said shafts. Said housing carries a dog adapted to engage either the main shaft or the auxiliary shaft. Hydraulic power controlled by a piston valve is employed to lock the clutch operator in adjusted position.

In the Ipreferred embodiment of the invention shown in Figs. 1-7, both inclusive, the clutch operator comprises a cylindrical sleeve l0 mounted slidably upon a power shaft Il. Said power shaft is coupled to a source of motive power, such as an internal combustion engine (not shown).

One portion of the power shaft Il is provided with left-hand threads I6 and another portion of said shaft is provided with right-hand threads il. (While square threads have been shown, any type of thread can be employed.) The sleeve ID is free to slide along the shaft Il and over the threaded portions thereof, and does not rotate with said shaft. A plurality of cylindrical bosses I2 and I3, which are formed integral said sleeve I0, are provided with an axial bore and project from spaced positions on the periphery of said sleeve to carry the dogs and cam bar hereinafter described. A plurality of dogs I4 and I5 are each cylindrical in form and fit slidably Within the bores of the bosses I2 and I3respectively.., Faces of the dogs I4 and I5 are provided With teeth I8 and I9 respectively, said teeth being cut to mesh with the shaft threaded portions I6 and I1 respectively.

The boss I2 is provided with longitudinal apertures or slots 2E) and 2l, one on eachside. thereof,

the plane of said slots being radial the axis ofv the sleeve I0. The boss I3: is providedwith. correspondingly disposed longitudinal apertures or slots 22 and 23. The dogs I4 and I5 are provided with transverse slots 24 and. 25-respectively. Said slots 24 and 25 are adapted to be, aligned with ther slots in the bosses in which they are mounted so asfto carry a cam bar 26.

Said cam bar 26 extendsy through the slots of the bossesv and dogs, preventing rotation of the dogs in their respective bosses, while permitting movement of said dogs parallel tothe longitudinal axis. of their respective bosses. The dimensionsof said cambar are such that said bar holds both of the dogs out ofK contact with the shaft I I when` the sleeve I- is in a selected position and forces the face of one of the two dogs to mesh with a threaded portion of the shaft while locking the other dog out of engagement With said shaft, the direction of movement of the sleeve IIJ determining whether the face ofthe dog I4 or of thedog I will engage the shaft I I.

Said cam bar 2.6 is preferably flat and of uniform thickness, toy facilitate the slidable fit of saidcam bar inv the slots in the bosses and dogs. Said cam bar isv approximately twice the length ofthe sleeve Ill., and its maximum Width is somewhat less than the height of the slots 24 and 25. Said camibar 26 is` of reducedwidth at two intermediate portions 21 and 28, said portions being spaced a distan-ceapproximately equal to the spacing of the bosses I2 and I3, the length of each such portion being somewhat less than the diameter of the dogs I4 and I5. Cam surfaces 29 and 30 project from an edge of the intermediate portion 21 andl from an edge of the intermediate portion 28, respectively, to make the ends 3-I and 3.2. of said caml bar of greater width than the intermediate portion thereof. The opposite edges of the adjacent ends of they narrow intermediate portions are provided with cam surfaces 33- and 34 sov that the center portionr 35 of said cam bar is the same width as the ends 3I and 32 andv said center portion is offset from said ends. The cam bar is provided with a groove 36 longitudinal a side thereof and extending somewhat less than the lengthcf said bar. A leaf spring 31 secured to the sleeve I0 by any suitable means, such. as screws 38, has its end distal said sleeve riding in the groove 36. The spring 31 is so tensionedas to hold the cam bar 26 against the sleeve I.Il- While permitting the said bar to slide relative said spring.

A rack 39 secured to a stationary member I51 holds. thev sleeve I0, in operable position. Said rack 39. is disposed parallel to the longitudinal axis of the shaft I I, proximate the threaded portions of said shaft. Teeth 40 transverse the face of said rack adjacent the cam bar 26 are disposed along said. face a distance corresponding to the lengthof the threadedportions of the shaft II. The dogsv I4 and I5 are provided withA rectangular recesses 49 and 50 respectively in the ends of said dogs distal the shaft II, said recesses being disposed over the slots 24 and 25 respectively. Mounted slidably for reciprocable movement in these recesses are the rectangular stems 4I and 42 of pawls 43 and 44 respectively. These stems are providedwith transverse elongated apertures 45 and` 46l respectively, and retaining pins 41 and 49 span the recesses 49 and 55 respectively, passing through said apertures and having their ends retained in suitable apertures in the dogs, one end of each pin being threaded and one aperture ink each dog being tapped to receive said threaded end These pins limit the vertical movement of the pawls with respect to the dogs.

Leaf springs 5I and 52 are secured to the underside of the pawls 43 and 44 respectivly. Said leaf springs bear against the bottom of the recesses 4'9 and. 50vrespectively and serve to force the pawls out of their seats in the recesses in the dogs and into engagement with the rack 39. The distal ends of the pawls 43 and 44 are provided with transverse teeth 53. and 54V respectively. These teethY haveI one sloping side and one vertical side, which is beveled at the top, so that the pawl is adapted to slide in one direction relative the rack but cannot slide relative the rack in the opposite direction. rlhe teeth of one pawl are adapted to slide in one direction relative the rack and the teeth of the other pawl are adapted to slide in the opposite direction relative said rack, the respective vertical sides of said teeth facing in the direction in which the sleeve Will move when thev dog on which itis mounted engages the shaft.

An eye 55 is cast integral with the sleeve I0 and serves to connect said sleeve with the device that it operates.

A hydraulic cylinder 56 is providedY for moving the cam bar 26. This cylinder is disposed adjacentY the bosses I2 and I3, with its longitudinal axis parallel to thev longitudinal axis of the shaft II. Arms 51 and 58 integral with the rack 39 secure said cylinder 56 to saidl rack. A piston 59, having a piston ring 60, is attached to an end of a piston rod 6I for operation in the cylinder 56. Said piston rod 6I projects through a packing gland 62 in one end of the cylinder and a rectangular eye 63- on the other end of the rod 6I engages an arm 64 secured at an angle to the end of the cam bar 26. Fluid for operating the piston 59 is supplied through suitable conduits |19 and |80 to ports 65 and 66 respectively, which are disposed at opposite ends of the cylinder 56. Movement of the piston responsive to said fluid will therefore effect a corresponding movement of the cam bar 26 with respect to the sleeve I0.

The operation of the device described above is as follows: When the shaft I I is rotating in the direction indicated by the arrow in Fig. 1, the cam bar 26 is so positioned that dogs I4 and I5 are out of engagement with the shaft I I and the pawls 43 and 44 are engaged with the rack 39 so as to prevent any movement of the sleeve. When the piston in the hydraulic cylinder is moved in one direction by the force of the fluid, the cam bar 26 is moved in the same direction. The cam surface 33 then engages the lower edge of the slot 24 in the dog I4, forcing it to assume a position wherein the dog teeth I8 engage the left-hand threads I6 of the shaft II. This movement of the dog I4 also pulls the pawl 43 out of locking engagement with the rack 39, since the beveled top of the teeth will slide under the teeth 40 of the said: rack.. This movement of the cam bar 26 causesv its wide end 32 to move into slot 25 to prevent the dog I5 from engaging the teeth II -and to keep-the pawl 44 engaged with the rack 39, thereby preventing movement of the sleeve ID in the direction oppositethat above indicated.

Furthermovement of the cam vbar 26 in the direction aboveindicated forces the dog teeth I8 into mesh with the left-hand threads I6 and further lowers the pawl 43 so that it is completely out of contact with the rack 39. The wide center portion'35 of the cam bar enters the slot 24 to lock the dog I4 into engagement with the shaft II .Y 'If the crests of the dog teeth I8 arenot aligned with the adjacent roots of the left-hand threads I6 when the cam bar 2B is forced into the slot 24, the leaf spring 3l permits the said bar to ride up in the slots and ZI of the boss I2 until the shaft II rotates to a position where the teeth-will mesh. When such position is reached, the leaf spring 31 forces both the cam bar 26 and the dog I4 downward. Vertical movement of the cam bar 26 with respect to the piston rod BI is effected by means of the rectangular eye 63 on the end of the piston rod, which permits vertical play of the arm 64 of the cam bar 26.

The cam bar 26 is held stationary in the position to which it has been moved by piston 59 and the sleeve I0 moves in the direction above indicated, the dogs I4 and I5, sleeve I0 and leaf spring 3'I all sliding along the cam bar 25. This movement of the sleeve causes the sloping side of the pawl `teeth 54 to engage teeth 4I) of the rack 39, forcing the pawl 44 down into the rectangular recess 50 of the dog I5 and compressing the leaf spring 52. As soon as the pawl teeth 54 clear the teeth 40, the spring 52 forces them into engagement again.

The sleeve I0 continues to move in the same direction until the leading edge of the slot 24 in the dog I4 engages the cam surface 29, pulling the dog teeth I3 out of engagement with the lefthand threads I6 of the shaft II and raising the pawl 43 into contact with the rack 39. As the dog I4 moves on the cam surface 29, the slot 24 moves away from the wide center portion of the cam bar 26. Should the dog teeth I8 be released from the left-hand threaded portion I6 of the shaft by the cam bar 25 when the pawl teeth are not in mesh with the teeth 4D of the rack 39, the pawls 43 and 44 are forced down into their respective recesses 49 and 50 against lea-f springs 5I and 52 respectively. The force against which the sleeve I0 is moving will then cause the sleeve to drop back a sumcient distance to permit the pawls to mesh with the rack 33. At such time, the pawl 44 will prevent further movement of the sleeve. This final position is shown in broken lines in Fig. 5.

There is sufficient play between the cam surface 33 and the adjacent edge of the sloI'l 24 of dog I4 to permit the amount of slip of the sleeve necessary for the pawls to mesh with the rack without causing the slot 24 to engage the cam surface 33 to force the dog teeth into engagement with the left-hand threads I6.

The maximum distance the sleeve can slip back because of the failure of the teeth on the pawls to mesh with those of the rack is equal to the pitch of such teeth. For purposes of illustration, this slip is exaggerated in the drawings: In practice, this slip is reduced to a negligible amount by using teeth of a much smaller pitch. The slip can also be reduced by providing the pawls with staggered teeth, as shown in Fig. 7. In

rality of sections, with teeth of the outer sections 61 and 68 disposed commonly While the teeth of a medial section 59 are spaced intermediate the teeth of the outer sections. Each section is provided with leaf springs l0, 52 and 'II respectively, one end of each such spring being aixed suitably to the bottom end of its section. 'Ihis arrangement reduces the maximum slip in half, as it causes one set of teeth to mesh upon movement 'of the sleeve equivalent to one half of the pitch of the teeth. This type of construction can, of course, be modified to provide for teeth spaced at other degrees of relative stagger.

Movement of the sleeve IU in a direction opposite to that hereinabove described at length is effected by moving the cam bar 26 in said opposite direction. Then the dog teeth I9 engage the right-hand threads I'I of the shaft II and the dog I4 is locked out of engagement with the shaft II. The device then operates in the manner described above. f Y

`The depth of the threads on the shaft II decreases at the outer ends of each threaded portion `until the roots of such threads merge with the surface of the shaft. This permits the dog meshing with the threaded shaft to ride out of mesh'as it approaches the end of the threaded portionwithout damaging the device inthe event that cam bar 26 is displaced accidentally a greater distance than that for which it is de signed. As the dog rises, it forces the cam bar 26 up in the slots in the bosses against the pressure of leaf spring 3l.

When one of the dogs engages the shaft II, there is some tendency for the sleeve to rotate with the shaft. because of the friction between the several parts of the device and said shaft. But rotation of the sleeve is prevented by reason of [the fact that the cam bar 25 is attached to the piston rod, which is prevented from rotating because the cylinder 56 is fixed in position. However, if the tendency for the sleeve I6 to rotate is sufficiently great, some additional means for preventing such rotation can be provided. For example, the eye 55, or some equivalent structure, can operate in a slot on some adjacent stationary member (not shown).

The modification illust-rated in Figs. 8 to` 11, both inclusive, employs a `hydraulic cylinder and piston to lock thedevice in any adjusted position and a different means for taking power from the drive shaft.

The power-driven shaft 'I2 has threads I3 along a portion of the length thereof. A back shaft 'I4 disposed parallel to shaft 'I2 and carried proximate thereto is journaled in a bracket 'I5 adapted to be affixed to some stationary member. A screw 73 in a tapped aperture in said bracket adjacent the shaft I4 projects into a peripheral groove 'II cut into the shaft 14, thus preventing movement o f said shaft in the direction of its longitudinal axis. Shaft 'I4 is provided with threads 'I8 corresponding in pitch t0 the threads 13. The shafts l2 and 'I4 are coupled through gears 'I9 and 80, which have a ratio of 1:1, so that the shafts rotate at the same speed and in opposite directions. Said shafts support the housing I, hereinafter described.

The housing l comprises sleeves 82 and 83 having cylindrical bores 84 and 85 respectively runningT the length of said sleeves and adapted to carry the shafts 'I2 and 14 rotatably therein. The housing also has a hydraulic cylinder 86 integral therewith and disposed below the sleeve 83. Walls lioining the sleeve 82 and the cylinder 86 form a reservoir 81 (see Fig. 9) and the Space between the sleeves is bridged by a wall 88 running the length of the housing. AV cover plate 89; is: secured above said space by webs 90 and9l. A lug: |49 serves as a means for couplingl the housing to the device to be operated.

The sleeves 82 and 83 are provided with apertures 92 and 93 respectively (see Fig. l0), said apertures being disposed in adjacent walls. These apertures face each other near the center of the sleeves and the aperture 92 is provided with vertical flanges |04 and |05, the aperture 93 having similar flanges |06 and |01. A dog 94 mounted in these apertures is guided by the anges and is reciprocable relative the shafts. Said dog 94r is of a length permitting it to just clear each shaft when positioned therebetween. The end of the dog 94 adjacent shaft 12 is provided with teethv 95 adapted to mesh with the threads 13'. The other end carries teeth 96 adapted to mesh with the` threads 18 on the shaft 14. The dog is provided with a transverse rectangular opening 91 in which are mounted levers 98 and 99, said levers having fulcra |00 and ||l|l respectively. Said fulcra are disposed at points diagonal to each other and the free ends of said levers are adapted to extend in opposite directions within the opening 91. Leaf springs |02 and |03 are aiiixed to the respective levers and bear against the sides of the opening 91 to urge the free ends of the levers away from the sides of the opening and toward the center thereof.

A cam bar |08 adapted to operate the dog 94 comprises an elongated member of uniform thickness, rectangular in cross-section and having a center portion |09 of reduced width. The length of this portion |09 is slightly greater than the width of the dog 94. Cam surfaces and project from opposite edges of the center portion |09 to provide end portions ||2 and ||3 of increased width and offset with respect to eachother. A groove ||4 medial the face of the cam bar |08 extends substantially the length of said bar. The webs 9|]y and 9| are provided with apertures and ||6 respectively, said apertures having a configuration corresponding to the cross sections of thev end portions I2 and ||3 of the cam bar |08. Said bar is mounted slidably in the apertures ||5 and H6 and is provdedwith keys ||1 projecting into the groove 4 to prevent lateral displacement thereof.

The cam bar |08 projects through the opening 91 in the dog 94 and between the levers 98 and 99. The free ends of said levers bear against the oppositeA edges of said bar. When the center portion |09 of the bar is Within the opening' 91, the dog 94 isv centered with respect to the shafts 1:2 and 14 and does not engage either.

A xed hydraulic cylinder I|8, secured to the bracket by means of a bracket |9, is disposed in, spaced relation to the cover plate 89 with its longitudinal axis parallel to the cam bar |08 and constitutes the means for moving said bar. A piston |20, provided with a, piston ring |2| is positionedin said cylinder and affixed to a piston rod |22. The said piston rod is connected to the end of the cam bar |08, passing through a. suitable packing gland |23 in the end of the cylinder. Conduits |24 and |25 connected to opposite ends of the cylinder supply fluid for actuating the piston.

The hydraulic cylinder 86 contains a piston |26 connected to a piston rod |28 that projects throughl the, end of the cylinder and is secured infixed position: bybeingv bolted tol the bracket 15, as shown in Fig. 8. Said piston is provided with a piston ring |21 adapted to prevent bypassing ofthe hydraulic fluid. Said piston rod passes through a suitable packing gland |29.

As shownA in Fig. 9, the flow of fluid into and out of the cylinder 86 is controlled by a piston valve |30 housed inthe reservoir 81. This valve has a cylinder I3| provided with `a, plurality of circumferentially disposed sets of ports |32, |33, |34, |35 and |36, spaced along the length ofv said valve. Ports |33 and |35 connect respectively with collecting conduits |31 and |38 formed integral with the cylinder |3| and are provided with openings |39 and |40 for conduits |4| and |42 respectively. The pistons |43, |44 and |45, which control the ports, are mounted on a common piston rod |46 and move as a unit, and piston rings on each of the pistons serve to prevent fluid leakage. Piston |44 controls the flow of fluid through ports |34 and pistons |43 and |45 control the fiow of fluid through ports |32 and |36 respectively.

It will be seen that when the valve is in the position shown in Fig. 9 no iiuid can pass therethrough. However, when the pistons are moved in either direction from that position, ports |35 connect with ports |34 and ports |33 connect with ports |32, permitting a flow of iiuid therethrough. Conduit |4| connects ports |33 to one end of the cylinder while conduit |42 connects ports |35 with the other end of said cylinder. The piston rod |46 is bolted to an end of a bar |41, the other end of said bar being secured rigidlyv to the center of the lower side of the dog 94. An aperture |48 in the wall 88 is of sui-licient size to permit lateral movement of the bar |41 projecting therethrough. The reservoir 81 and the cylinder 86 are filled with a suitable fluid.

As shown in Figs. 8, 9 and 10, to effect movement of the housing 8|, the cylinder ||8 is energized by fluid under pressure supplied through conduit |24, which forces the piston |20 to move in one direction. As the cam bar 08 is affixed to the piston rod |22, it moves in the same direction, sliding in apertures ||5 and ||6. In this operation, the free ends of the lever 99 rides up the cam surface and said lever rotates about the fulcrum IUI in a counter-clockwise direction, compressing the leaf spring |03. This causes the dog 94 to move the teeth 96 thereon into contact with the threads 18 on the shaft. If they do not mesh at once, the leaf spring |03 is further compressed, thereby increasing the force acting on the dog. As soon as the shaft rotates to a position at which said teeth and threads mesh, the leaf spring |03 forces said teeth and threads into engagement. The levers 98 and 99 are subjected to equal degrees of compression by their respective leaf springs |02 and |03, thereby positioning the dog 94 symmetricaly with respect to the end portion ||2 of the cam bar |08. Since said end portion is offset towards the back shaft 14, the dog is retained in engagement therewith. This lateral movement of the dog also operates piston valve |30 through the bar |41 and piston rod |46 to move the pistons |43, |44 and |45 and to place ports 33 in communication with ports |34 and ports |35 in communication with ports |33. The housing then moves as the dog 94 slides along the cam bar |08 and the cylinder 86 slides over the piston |26. Fluid thereupon fiows out of the end of the cylinder 86 through conduit |4|, through ports |33 and out ports |34 to the reservoir. Similarly, fluid enters the other end of the cylinder 86 by owing from the reservoir 81 through ports |36 and |35 and through conduit |42.

- The dog contirnles to move along the cam bar |68 until it reaches the centre portion |69. At such time, the levers 98 and 99 disengage the dog 94 from the shaft and retain said dog in disengaged postion.

The operation of the device occurs substantialy as follows: When the power driven shaft 12 and the back shaft 14 coupled thereto are rotating in the direction indicated by the arrows in Fig. 8, and the dog 94 is not engaging either shaft, the levers 96 and 99 engage the center portion |09 of the cam bar |68 and serve to center said dog with respect to said shafts. The piston valve |39 is held by the bar |41 in such a position that the flow of fluid to and from the cylinder 86 is out off, thereby locking the housing in position with respect to the piston and preventing movement thereof in an axial direction. In reaching such centered position, the dog 94 moves the piston valve |39 so as to close the ports anpl prevent any fluid from flowing into or out of the cylinder 86, thus locking said housing against any movement. Y

The movement of the housing in one direction is eifected by moving the cam bar |08 in that direction to force the dog 94 into engagement with the power-driven shaft 12 and the piston valve is moved in the opposite direction, which permits a flow of fluid into and out of the cylinder 86. The operation of the parts will be substantially the same as that described above.

While a piston valve has been disclosed in the drawings, other types of valves can be employed for controlling the ow of uid intovand out of the cylinder. For example, simple petcocks, operable by the bar |41, can be attached to the ends of the conduit, or the ends of the conduits |l|| and |42 can be connected to a petcock operable by the bar |41. In this latter means, the need for a reservoir 61 is avoidedas the fluid in the cylinder 86 passes from one end thereof to the other through said conduits.

An advantage of the type of clutch operator shown in Figs. 8 to 1l, both inclusive, is that it can be comparatively short in overall length, thus simplifying the task of installation and adapting it to use with marine motors. The hydraulic cylinder used to lock the housing in position when it is not being moved avoids the possibility of the slip encountered in the first-described device when the rack takes hold after release of the dog.

Fig. ll illustrates a combined motor control and clutch operator control system adapted to keep the motor speed relatively low while the clutch operator is activated and after operation of the clutch to permit the throttle to be operated while the clutch operator control is locked inposition, in order to prevent any movement thereof while the throttle is being operated.

A motor |56 is provided with a throttle |5| having a lever |52 connected to the piston |1| of a hydraulic cylinder |53 through suitable linkages |54 and |55. Said cylinder |53 is affixed to a stationary part of the motor, as shown, The motor shaft |56 carries a clutch operator similar to that shown in Fig. l, the rack 39 and cylinder 56 being xed to a stationary part of the motor by bracket |82. The clutch housing |58 has a clutch lever |59 connected to the clutch operator by a link |66. The control member, which may be positioned remotely, comprises a drum |6| mounted suitably for rotation about its axis.

(Said mounting is not shown in the drawings.) The drum |6| is provided with a handle |62 by which it is rotated, and the periphery of said drurn has a throttle groove |63 cut therein. The medial portion of this groove parallels the ends of the drum while the end portions of said groove diverge towards an end of said drum. A piston rod |65 carries a roller bearing (not shown) on a pin |64 which projects into the groove |63. Said piston rod carries a piston |66 mounted for reciprocal movement in a hydraulic cylinder |61. Conduits |68 and |69 connect opposite ends of the cylinder |61 to opposite ends of the cylinder |53. A needle valve |16 is adapted to control the rate of flow of fluid from the cylinder |51 and hence controls the speed of operation thereof.

A clutch operator groove |12 is cut in the periphery of said drum, the medial portion thereof being helical in form and coextensive with the medial portion of groove |63. The end portions of the groove |12 parallel the ends of the drum and are coextensive with the end portions of the groove |63. A second hydraulic cylinder |13 is aligned axially with cylinder |61 and is provided with a piston |14. Said piston |14 is provided with a piston rod |15 and roller bearing |16 carried by pin |11 projecting into groove |12. Packing lgland |18 is adapted to prevent leakage around the piston rod |15. The piston rod |65 is provided similarly with a packing gland. Conduits |19 and |86 connect the opposite ends of the cylinder |13 to opposite ends of the cylinder 56 of the clutch operator. Aneedle valve 18| is adapted to control the flow of fluid in the cylinder |13. All of the cylinders and conduits are filled with a suitable fluid.

In neutral position, when the clutch operator is inoperative, the roller bearing attached to the piston rod |65 is equidistant from the diverging portions of the groove and the piston rod |65 is held adjacent one end of the cylinder |65. The roller bearing |16 is positioned correspondingly in groove |12 equidistant from the ends of the medial portion of said groove and the piston |14 is held medial the cylinder |13. The control cylinder |53 has its piston adjacent the end thereof that is connected to the end' of the cylinder |61 distal piston |66. This position of the throttle control piston corresponds to idling speed of themotor-movement to the left increases the motor speed. The piston in the control cylinder 56 is positioned centrally.

When it is desired to engage the clutch, the handle |62 is pushed in a clockwise direction to rotate the drum. As the roller on piston rod |65 operates in the medial portion of groove |63, the motor speed does not change during the first movement of the drum. Roller bearing |16, being in the helical portion of groove |12, moves the piston |14 to the left, forcing the fluid through conduit |19 into the left end of cylinder 56. This operates the clutch operator, in the manner hereinabove described, to engage the clutch mechanism through link |60 and clutch lever |59. Thus, the clutch operator functions when the motor |50 is running at low speed. Upon further rotation of the drum |6|, the roller bearing |16 passes into the'lower end of the groove |12. This change produces no further movement of the piston |14. At the same time, the helical portion of the groove |63 operates to` move the piston |66 to the right, forcing fluidthrough conduit |69 to the right end of cylinder |53 to operate the piston |1| connected to the throttle, thereby increasing the speed. The greater the 11 movement of the drum, the greater will be the speed, since movement of the piston I-H is proportional to the motor speed.

In stopping, the converse of the above procedure is followed: The drum is rotated counterclockwise to slow down the motor by means of the cylinder |61 and the piston |1| before causing the clutch operator to return to neutral or initial position under the influence of cylinders |13 and 56. A In reversing, substantially the same procedure is followed: The drum is rotated counterclock- Wise, causing piston |14 to move to the right and forcing fluid into the right end of cylinder 56, which actuates the clutch operator, moving the clutch to reverse position. During this operation, the motor is idling. Upon completion of the operation of the clutch and continued rotation of the drum, the speed of the motor is increased while the clutch operator is maintained in the position to which it has been moved. In stopping, the speed is reduced before the clutch operator is energized to move the clutch to neutral position.

The needle valves |8| and |1 control the rate of flow of the uid from their respective cylinders and hence control the speed of operation of the system. As the pistons are not moved at the same time, needle valve |8|, which controls the speed of operation of the clutch operator, can be set independently for a different rate` of speed than the throttle controlled by valve |10.

Various modifications and changes can be made in the device without departing from the scope of the invention.

The invention described herein may be manufactured and used by or for the Government of the United States of America for governmental purposes without the payment of any royalties thereon or therefor.

I claim:

l. Mechanism comprising a rotatable shaft having right-hand threads and left-hand threads, means to rotate said shaft, linearly movable thread-engaging elements adapted respectively to engage said threads and a cam bar extending along the threaded portions of said shaft, said cam bar having a portion of reduced width and being thereby adapted to hold said elements out of contact with said threads at one time and to hold either but only one of said elements in contact With said threads at another time, said cam bar being adapted to move said one element out of contact with said threads and adapted to be motivated therefor by said one element moving with said threads for a predetermined distance.

2. Mechanism comprising a rotatable shaft having right-hand threads and left-hand threads, means to rotate said shaft, linearly movable thread-engaging elements adapted respectively to engage said threads and a cam bar extending along the threaded portions of said shaft, said cam bar having a portion of reduced Width and being thereby adapted to hold said elements out of contact with said threads at one time and to hold either but only one of said elements in contact with said threads at another time, said cam bar being adapted to move said one element out of contaotwith said threads and adapted to be motivated therefor by said one element moving with said threads for a predetermined distance, and locking means operated by said cam bar at the end of said predetermined 12 time to restrain said element against further linear motion.

3. Clutch-actuating mechanism comprising a shaft having right-hand and left-hand threaded portions, a housing movable axially thereon, thread-engaging elements adapted respectively to engage said threaded portions and controlled by a cam bar for movement parallel to said shaft so that said elements are held out of contact with said shaft by said cam bar in one position and so that one element engages said shaft in another position of said cam bar, so that rotation of said shaft causes axial movement of said element and housing until said element reaches a portion of said cam bar that releases it, a clutch operator actuated by said housing. and a rack and pawl adapted to hold said clutch operator in position when said element is released from said shaft.

4. Clutch-actuating mechanism comprising a shaft provided with a medially disposed lefthand threaded portion and an adjacent medially disposed right-hand threaded portion, the roots of said threads each decreasing from full depth at their adjacent ends to convergence with the periphery of said shaft, a, cylindrical sleeve mounted slidably on said shaft and adapted to slide freely along the threaded portions thereof, a pair of spaced cylindrical bosses formed integral said sleeve and projecting therefrom, threadengaging elements positioned slidably in axial bores of said bosses, said elements having toothed faces adapted to mesh with threaded portions of the shaft, slots in said bosses and elements being adapted to be aligned to carry a common cam bar, a cam bar extending through said slots adapted to retain said elements out of contact with said shaft and to effect contact of one of said elements with said shaft while retaining the other element out of contact therewith, a leaf spring secured to said sleeve having its end distal said sleeve riding in a medial longitudinal groove in said cam bar and adapted to hold said cam bar against said sleeve while permitting said bar to slide relative said spring, a rack parallel the longitudinal axis of said shaft secured to a stationary member, transversely disposed teeth on the face of said rack, pawls seated in said elements adapted for limited reciprocaton therein radial said shaft, teeth on the faces of said pawls adapted tov engage the teeth of said rack upon movement of the sleeve in one direction and to slide over the teeth of said rack upon movement of said sleeve in the opposite direction, means forcing said teeth against the teeth of said rack. and hydraulic means for moving said cam bar relative said sleeve.

5. Clutch-actuating mechanism comprising a shaft having a left-hand threaded portion and a right-hand threaded portion. a sleeve mounted slidably on said shaft for movement over the said threaded portions, a pair of bosses carried by said sleeve, each boss having an axial bore, thread-engaging elements positioned slidably in said bores, said elements having toothed faces adapted to mesh with said threaded portions, slots in said bosses and elements, a cam bar extending through said slots adapted to retain said elements out of contact with said shaft and to effect contact of one of said elements only with said shaft, a leaf spring secured to said sleeve and having its end distal said sleeve riding in a groove in said cam bar to hold said cam bar against said sleeve while permitting said bar to slide relative said spring, a rack having transverse teeth positioned parallel to said shaft and secured to a stationary member, pawls seated in said elements and reciprocable therein radial said shaft to engage the teeth of said rack upon movement of the sleeve in one direction and to slide over said teeth upon movement of said teeth in the opposite direction, means forcing said pawls against the teeth of said rack, and means to move said cam bar relative said sleeve.

6. Clutch-actuating mechanism comprising a shaft having left-hand and right-hand threaded portions, a sleeve mounted slidably on said shaft, a pair of bosses carried by said sleeve, each boss having a bore, thread-engaging elements positioned slidably in said bores and adapted to mesh with said threaded portions, slots in said bosses and elements, a cam bar extending through said slots and having enlarged portions adapted to move said elements into engagement with said threaded portions selectively, a spring carried between said sleeve and said cam bar and adapted to hold said cam bar against said sleeve while permitting said bar to slide relative said spring, a rack secured to a stationary member, pawls seated in said elements and reciprocable therein radial said shaft to engage said rack upon movement of the sleeve in one direction and to slide over said teeth upon movement of said teeth in the opposite direction, means forcing said pawls against the teeth of said rack, and means to move said cam bar relative said sleeve.

7. Clutch-actuating mechanism comprising a shaft having left-hand and right-hand threaded positions, the distal portions of the roots of said threads each decreasing to convergence with the periphery of said shaft, a sleeve mounted slidably on said shaft, a pair of bosses carried by said sleeve, each boss having a bore, thread-engaging elements positioned slidably in said bores and adapted to mesh with said threaded portions,

slots in said bosses and elements, a cam bar extending through said slots and having enlarged portions adapted to move said elements into engagement with said threaded portions selectively, a spring carried between said sleeve and said cam bar and adapted to hold said cam bar against said sleeve while permitting said bar to slide relative said spring, a rack secured to a stationary member, pawls seated in said elements and reciprocable therein radial said shaft to engage said rack upon movement of the sleeve in one direction and to slide over said teeth upon movement of said teeth in the opposite direction, means forcing said pawls against the teeth of said rack, and means to move said cam bar relative of said sleeve.

ERWIN J. HAUBER.

REFERENCES CITED The following references are of record in the le of this patent:

UNITED STATES PATENTS Number Name Date 691,968 Paine Jan. 28, 1902 699,963 Lines May 13, 1902 929,520 Truxal July 27, 1909 1,134,085 Kroeze Mar. 30, 1915 1,310,752 Hand July 22, 1918 1,346,997 Van Berkel July 20, 1920 1,409,090 Glasser Mar. 7, 1922 1,421,163 Burrows June 27, 1922 2,082,679 Brown July 1, 1937 2,084,321 Corradino June 22, 1937 2,112,835 Ekstromer Apr. 5, 1938 2,226,591 Swenson Dec. 31, 1940 2,232,790 Kress Feb. 25, 1941 2,245,457 Brassell June 10, 1941 2,441,596 Reitter May 18, 1948 

